US5007400A - Hydraulic control device for fuel injection systems of internal combustion engines - Google Patents

Hydraulic control device for fuel injection systems of internal combustion engines Download PDF

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Publication number
US5007400A
US5007400A US07/328,396 US32839689A US5007400A US 5007400 A US5007400 A US 5007400A US 32839689 A US32839689 A US 32839689A US 5007400 A US5007400 A US 5007400A
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US
United States
Prior art keywords
piston
control
work chamber
fuel injection
stepped
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/328,396
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English (en)
Inventor
Rudolf Babitzka
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH, STUTTGART, FED. REP. OF GERMANY reassignment ROBERT BOSCH GMBH, STUTTGART, FED. REP. OF GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BABITZKA, RUDOLF
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Publication of US5007400A publication Critical patent/US5007400A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the invention is based on a hydraulic control device as defined hereinafter.
  • hydraulic control devices that operate with closed fluid-filled chambers and in which pistons and valve faces are acted upon, the basic relationship between the fluid-impinged surface area and the forces derivable from the fluid pressures and surface areas always presents problems when the time factor plays a role.
  • the same force for instance can be attained with a low pressure and a large surface area or conversely with a high pressure and a small surface area; but for the time factor, it is the control of the volume or in other words the quantity flowing out per unit of time that is definitive.
  • valves used for control should have an extremely short opening and closing time factor, on the one hand, and on the other should have as little flow resistance, or in other words as small a control cross section, as possible.
  • a hydraulic control device of this kind becomes problematic if large volumes of fluid at high pressure must be controlled at very short time intervals, as is the case for instance with fuel injection, when the control must be effected in less than a millisecond and must vary with the rpm.
  • the fuel injection can be interrupted by relieving the pressure of the pump work chamber via a relief conduit; this conduit is controlled via a magnetic valve.
  • the movable valve element of the magnetic valve is acted upon directly by the high pressure of the pump work chamber, so when the valve is closed, if no outflow is to take place, then depending on the functional surface area operative in the opening direction of the movable valve element, considerable forces must be brought to bear to keep the valve closed.
  • a magnetic valve that is open when there is no current through it which for safety reasons is the kind of valve usually used for this purpose, the energy consumption of the magnet is proportional to the forces required to keep the valve closed.
  • the opening time cross section which is a product of the opening time and the opening cross section, that is required for control
  • a relatively large cross section must usually be selected, given the short times that are available; this means large, expensive magnets and a correspondingly high consumption of electricity.
  • a pressure line branches off from the pump work chamber, and the fuel is supplied via this line to a deflecting piston, which is displaced by the feed pressure of the injection pump whenever the magnetic valve is open; the space on the back side of the deflecting piston is pressure-relieved by the magnetic valve.
  • This piston is loaded by a restoring spring, which piston injects this fuel received as it deflects into the combustion chamber of the engine via the injection nozzle toward the end of the injection and after the end of the high-pressure feeding. The result is a longer injection duration and quieter engine idling.
  • the hydraulic control according to the invention has an advantage over the prior art that the fluid volume that must flow through the valve within a predetermined period of time for a predetermined displacement of the control piston is reduced, by comparison with the volume that is aspirated and pre-stored in the control piston when it moves, by the ratio of the size of the working face with that of the control face.
  • the pressure in the work chamber increases inversely proportionally to the control chamber pressure; that is, the pressure in the work chamber is greater, by the ratio of the control face to the working face, than in the control chamber.
  • This pressure in the work chamber in turn acts upon the movable valve element of the valve, so that their closing pressures must be adapted to that pressure. Because of the ratio of the surface area of the working face and the control face, which is greatly diminished by the volume to be controlled by the valve, the opening cross section of the valve can be decreased accordingly as well; it now proves, advantageously, that if the closing force remains unchanged, the use of the stepped piston makes it possible to attain a time/cross section gain corresponding to the surface area ratios.
  • This advantage is particularly effective in fuel injection pumps for internal combustion engines in which the duty cycles are extremely short - as in a four-cylinder engine at 4000 rpm, which is equivalent to approximately 66 duty cycles of the deflecting piston per second; moreover, this varies as a function of the rpm.
  • a magnetic valve is used as the control valve, so that the smaller adjusting forces required as a result of the invention are particularly advantageous, because the expense for generating a magnetic force increases not only with the structural volume but also in terms of cost in proportion to the magnitude of the adjusting force.
  • the stepped piston is spring-loaded in the direction of the pump work chamber, so that after the reduction of the pressure in the pump work chamber it is automatically thrust back into an outset position.
  • the stepped piston may be used as a deflecting piston or for controlling a relief conduit.
  • the control piston functioning as a deflecting piston is displaced counter to the restoring force by the pressure in the pump work chamber as soon as the valve opens; in this process, a volume is stored in front of its control face that is then pumped back again by the control piston toward the end of the injection.
  • this return pumping leads directly via the injection valve to injection, or this stored quantity is supplemented for the injection by the injection pump governor. In either case, this device attains a prolongation of the injection duration, which is particularly significant in idling, so as to attain smooth engine operation as a result.
  • the small control valve controls a large outflow cross section at the control piston.
  • FIG. 1 shows a distributor injection pump in longitudinal section, having the stepped piston as a pre-controlled valve
  • FIG. 2 on a larger scale, shows a detail pertaining to the invention of the distributor pump of FIG. 1, with the stepped piston functioning as a deflecting piston.
  • a pump piston 1 also serving as a distributor is set into simultaneously reciprocating and rotary motion by a drive shaft 2 with the aid of a cam drive 3.
  • fuel is pumped out of a pump work chamber 4 via a longitudinal distributor groove 5 to one of a plurality of pressure conduits 6, which are distributed at equal angular intervals about the pump piston 1, each leading to one combustion chamber, not shown, of an internal combustion engine.
  • the pump work chamber 4 is supplied with fuel via a suction conduit 7 from a fuel-filled suction chamber 8 located in the housing of the fuel injection pump, in that during the intake stroke of the pump piston 1, the suction conduit 7 is opened up by means of longitudinal control grooves 9 provided in the pump piston 1.
  • the number of control grooves 9 is equivalent to the number of pressure conduits 6 and hence to the number of compression strokes executed per rotation of the pump piston.
  • the quantity to be injected, which is pumped per stroke into each of the pressure conduits 6, is determined by the axial position of a governor slide 11 disposed surrounding the pump piston 1. This axial position is determined by an rpm governor 12 and an arbitrarily actuatable adjusting lever 13, taking into account the rpm and load at the time (the load may for instance correspond to the position of the gas pedal of the motor vehicle).
  • the suction chamber 8 is supplied with fuel from a feed pump 14, which is driven by the drive shaft 2 and is supplied with fuel from a fuel tank 15 and a suction line 16.
  • a pressure control valve 17 By means of a pressure control valve 17, the outset pressure of the feed pump 14 and hence the pressure in the suction chamber 8 are controlled; this pressure increases with increasing rpm in accordance with a desired function. Because both the cam drive 3 and the rpm governor 12 are disposed in the suction chamber 8, they are exposed to this pressure on all sides and are also lubricated on all sides by this fuel.
  • the cam drive 3 has a roller ring 19 with rollers 18, which is supported in the housing such as to be rotatable about a certain angle; the rollers 18 are supported in the U-shaped cross section of roller ring 19.
  • the roller ring 19 is coupled in a manner fixed against relative rotation with an injection adjuster piston 22 via an adjusting bolt 21.
  • This injection adjuster piston 22 is shown rotated by 90° in the drawing; that is, it operates at right angles to the plane of the drawing.
  • a claw coupling is provided in the internal bore of this roller ring 19; claws 23 of the drive shaft 2 located on the drive side mesh with claws 24 of the pump and distributor piston 1 on the power takeoff side, so that the pump and distributor piston 1 can execute a reciprocating motion during its rotation, independently of the drive shaft 2.
  • a face cam disk 25 is disposed on the pump piston 1, which with its face having face cams 26 rolls on the rollers 18; the number of face cams corresponds to the number of pressure conduits 6.
  • the cam race of the face cam disk 25 is pressed by springs 27, only one of which is shown, against the rollers 18.
  • a high-pressure control line 28 branches off from the pump work chamber 4 and leads to a control piston 29, which is stepped and is axially displaceably guided in a corresponding stepped bore 30; the end face of the piston 29 having the larger diameter, here identified as the control face 31, is oriented toward the pump work chamber 4.
  • the second end face of the piston having the smaller diameter and in this case identified as the working face 32, defines a segment of the stepped bore 30, which is closed by a magnetic valve 33 and the area defined by the small end of the piston and the stepped bore is identified as the work chamber 42.
  • the control piston 29 is also urged in the direction of a control chamber 40 by a spring 34 which control chamber is defined by the end face 31 and the large end of the stepped bore.
  • the magnetic valve 33 is constructed such that it is open when there is no electricity applied to the coil 35.
  • the valve 37 opens and the spring 34 forces the control piston 29 to the left, fuel at the pressure of the suction chamber 8 is admitted to the work chamber 42 via the conduit 38.
  • the magnet coil 35 of this magnetic valve 33 is excited, the movable valve element 36 of the magnetic valve is forced onto the valve seat 37 and the work chamber 42 is closed.
  • the functional face 43 of the movable valve element 36 that is thereafter acted upon from the work chamber and operates in the opening direction is smaller than the working face 32 of control piston 29 and determines the maximum opening cross section of the magnetic valve 33.
  • control face 31 of the control piston 29 having the larger diameter, oriented toward the piston 39 controls an entrance 41 of a second relief conduit 44, so that after the reciprocation of the control piston 29 to the right, the pump work chamber 4 is relieved of pressure in favor of the suction chamber 8. As a consequence, no pressure can build up in the pump work chamber, and the engine stops.
  • the second exemplary embodiment of the invention is similar in design to the first, but with the distinction that the control piston 29 here functions as a deflecting piston, and the magnetic valve 33 is closed when it is without current.
  • the control piston 29 here functions as a deflecting piston
  • the magnetic valve 33 is closed when it is without current.
  • the movable valve element 36 lifts from the valve seat 37', and the fuel under pressure in the pump work chamber displaces the control piston 29 toward the right, whereupon the working face of the control piston 32 positively displaces fuel out of the work chamber 42' and through the relief conduit 38 to the pump suction chamber.
  • This fuel volume, collected in the manner of a reservoir in front of the control face 31, is then, after the end of the high-pressure phase in the pump work chamber 4, while the pump piston 1 is at rest or in the ensuing intake stroke, is pumped back into the pump work chamber 4 or is pumped via it and one of the pressure channels 6 to the engine, where it is injected.
  • This quantity can also be supplemented at the pump by the governor.
  • This method of temporarily storing a certain quantity of fuel during the injection is known as the quiet-idle method, because it prolongs the injection duration and thus makes quiet idling of the engine attainable.
  • the opening cross section D ⁇ h/2 4 ⁇ 0.4/2 ⁇ 2.5 mm 2 .
  • the opening cross section would be:
  • Naturally influence can also be exerted by reducing the seat diameter and/or varying the opening stroke, in each case with a corresponding effect on the parameters.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US07/328,396 1988-06-11 1989-03-24 Hydraulic control device for fuel injection systems of internal combustion engines Expired - Fee Related US5007400A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3819996A DE3819996A1 (de) 1988-06-11 1988-06-11 Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
DE3819996 1988-06-11

Publications (1)

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US5007400A true US5007400A (en) 1991-04-16

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US07/328,396 Expired - Fee Related US5007400A (en) 1988-06-11 1989-03-24 Hydraulic control device for fuel injection systems of internal combustion engines

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US (1) US5007400A (de)
EP (1) EP0346607A3 (de)
JP (1) JPH0233462A (de)
DE (1) DE3819996A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5146895A (en) * 1989-12-29 1992-09-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US5150688A (en) * 1989-10-20 1992-09-29 Robert Bosch Gmbh Magnet valve, in particular for fuel injection pumps
US5443049A (en) * 1992-02-19 1995-08-22 Lucas Industries Public Limited Company Fuel pumping apparatus
US6152708A (en) * 1997-04-04 2000-11-28 Robert Bosch Gmbh Fuel injection pump for an internal combustion engine
US6394072B1 (en) * 1990-08-31 2002-05-28 Yamaha Hatsudoki Kabushiki Kaisha Fuel injection device for engine
US6725843B2 (en) * 2001-12-04 2004-04-27 Denso Corporation Fuel injection pump having feed pump assembly
US20180335005A1 (en) * 2015-11-26 2018-11-22 Yanmar Co., Ltd. Fuel injection pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4395987A (en) * 1980-04-26 1983-08-02 Diesel Kiki Co., Ltd. Distribution type fuel injection apparatus
US4480619A (en) * 1982-06-08 1984-11-06 Nippon Soken, Inc. Flow control device
US4546749A (en) * 1982-09-17 1985-10-15 Nippon Soken, Inc. Fuel injection apparatus
US4630588A (en) * 1982-11-25 1986-12-23 Mitsubishi Denki Kabushiki Kaisha Fuel injection timing control system
US4665875A (en) * 1984-12-20 1987-05-19 Lucas Industries Public Limited Company Liquid fuel pumping apparatus
US4753212A (en) * 1985-04-01 1988-06-28 Nippondenso Co., Ltd. High-pressure fluid control solenoid valve assembly with coaxially arranged two valves
US4779599A (en) * 1984-03-09 1988-10-25 Lucas Industries Public Limited Company Hydraulic mechanism
US4782803A (en) * 1986-06-24 1988-11-08 Diesel Kiki, Co, Ltd. Fuel injection control method for fuel injection pump
US4793315A (en) * 1984-07-13 1988-12-27 Lucas Industries Fuel pumping apparatus

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3211680A1 (de) * 1982-03-30 1983-10-06 Espenschied Helmut Dipl Ing Kraftstoffeinspritzsystem fuer brennkraftmaschinen
DE3302294A1 (de) * 1983-01-25 1984-07-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen
GB8430259D0 (en) * 1984-11-30 1985-01-09 Lucas Ind Plc Electromagnetically operable valve
DE3507853A1 (de) * 1985-03-06 1986-09-11 Robert Bosch Gmbh, 7000 Stuttgart Verfahren zur steuerung der kraftstoffeinspritzmenge
DE3715614A1 (de) * 1987-05-11 1988-11-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4395987A (en) * 1980-04-26 1983-08-02 Diesel Kiki Co., Ltd. Distribution type fuel injection apparatus
US4480619A (en) * 1982-06-08 1984-11-06 Nippon Soken, Inc. Flow control device
US4546749A (en) * 1982-09-17 1985-10-15 Nippon Soken, Inc. Fuel injection apparatus
US4630588A (en) * 1982-11-25 1986-12-23 Mitsubishi Denki Kabushiki Kaisha Fuel injection timing control system
US4779599A (en) * 1984-03-09 1988-10-25 Lucas Industries Public Limited Company Hydraulic mechanism
US4793315A (en) * 1984-07-13 1988-12-27 Lucas Industries Fuel pumping apparatus
US4665875A (en) * 1984-12-20 1987-05-19 Lucas Industries Public Limited Company Liquid fuel pumping apparatus
US4753212A (en) * 1985-04-01 1988-06-28 Nippondenso Co., Ltd. High-pressure fluid control solenoid valve assembly with coaxially arranged two valves
US4782803A (en) * 1986-06-24 1988-11-08 Diesel Kiki, Co, Ltd. Fuel injection control method for fuel injection pump

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5150688A (en) * 1989-10-20 1992-09-29 Robert Bosch Gmbh Magnet valve, in particular for fuel injection pumps
US5146895A (en) * 1989-12-29 1992-09-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US6394072B1 (en) * 1990-08-31 2002-05-28 Yamaha Hatsudoki Kabushiki Kaisha Fuel injection device for engine
US5443049A (en) * 1992-02-19 1995-08-22 Lucas Industries Public Limited Company Fuel pumping apparatus
US6152708A (en) * 1997-04-04 2000-11-28 Robert Bosch Gmbh Fuel injection pump for an internal combustion engine
US6725843B2 (en) * 2001-12-04 2004-04-27 Denso Corporation Fuel injection pump having feed pump assembly
US20180335005A1 (en) * 2015-11-26 2018-11-22 Yanmar Co., Ltd. Fuel injection pump
US10718305B2 (en) * 2015-11-26 2020-07-21 Yanmar Co., Ltd. Fuel injection pump

Also Published As

Publication number Publication date
JPH0233462A (ja) 1990-02-02
EP0346607A2 (de) 1989-12-20
DE3819996A1 (de) 1989-12-14
EP0346607A3 (de) 1990-02-14

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